EP3857068B1 - Compresseur à piston labyrinthe - Google Patents

Compresseur à piston labyrinthe Download PDF

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Publication number
EP3857068B1
EP3857068B1 EP19783448.4A EP19783448A EP3857068B1 EP 3857068 B1 EP3857068 B1 EP 3857068B1 EP 19783448 A EP19783448 A EP 19783448A EP 3857068 B1 EP3857068 B1 EP 3857068B1
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EP
European Patent Office
Prior art keywords
cylinder
piston
cylinder cover
labyrinth
piston compressor
Prior art date
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Active
Application number
EP19783448.4A
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German (de)
English (en)
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EP3857068A1 (fr
Inventor
Alexandre Voser
Reiner Schulz
Sandro BRUNNER
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Burckhardt Compression AG
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Burckhardt Compression AG
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Publication of EP3857068A1 publication Critical patent/EP3857068A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F04B39/041—Measures to avoid lubricant contaminating the pumped fluid sealing for a reciprocating rod
    • F04B39/045—Labyrinth-sealing between piston and cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0409—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0423—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0451—Particularities relating to the distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
    • F04B27/0536—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders with two or more series radial piston-cylinder units
    • F04B27/0538—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders with two or more series radial piston-cylinder units directly located side-by-side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/18—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use for specific elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F04B2015/081—Liquefied gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible

Definitions

  • Liquefied natural gas also known as “liquefied natural gas” or “LNG” for short, is natural gas that has been cooled to a temperature of at least -160 °C and that assumes a liquid state at these low temperatures.
  • LNG liquefied natural gas
  • the publication WO2009/112479A1 discloses a piston compressor for providing natural gas fuel, wherein this natural gas fuel is obtained by compressing the evaporation gas released from the liquid natural gas using the piston compressor.
  • Such a piston compressor which is very well-proven in itself, allows the evaporation gas of the liquid natural gas, which usually has a temperature of about -160 ° C at a pressure of usually 1 bar, to be compressed to a preferably variable final pressure in the range between 100 bar and 500 bar, preferably to a final pressure in the range between 210 bar and 350 bar.
  • a piston compressor has the advantage that natural gas can be sucked in and then compressed in a wide temperature range of preferably between -160 ° C and + 100 ° C.
  • Such a piston compressor is, for example, capable of to compress an input fluid having a temperature of -160 °C to a compressed fluid having a temperature of -40 °C.
  • DE 11 08 846 B describes a compressor in which the working piston, designed as a plunger piston, is guided in a bushing by a guide piston attached directly to it, or in which the working piston, designed as a plunger piston or disc piston, has sealing rings at the upper and lower ends, characterized in that discharge channels with outlet openings are arranged in the cylinder in such a way that the discharge channels are not overlapped by the upper edge and lower edge of the working piston or by the piston rings of the working piston during the stroke of the latter.
  • a cost-effective piston compressor in particular a labyrinth piston compressor, which is suitable for compressing a fluid that has a high temperature difference between the input fluid and the output fluid.
  • the object of the invention is to provide a piston compressor which, despite a high temperature difference between inlet and outlet, is suitable for compressing a fluid and which is economically advantageous.
  • a labyrinth piston compressor comprising a cylinder, a piston arranged in the cylinder and a piston rod, wherein the piston rod extends in a longitudinal direction and is connected to the piston, and wherein the piston is movable back and forth in the longitudinal direction within the cylinder, wherein the cylinder comprises a first cylinder cover, wherein an inlet valve and an outlet valve are arranged in the first cylinder cover, and wherein the inlet valve and the outlet valve are arranged symmetrically and inclined with respect to a plane of symmetry running longitudinally along the piston rod.
  • a labyrinth piston compressor comprises a piston and a cylinder, with a labyrinth seal being formed on at least the piston and the cylinder wall of the cylinder.
  • the labyrinth seal is a contact-free seal.
  • the sealing effect is based on the extension of the flow path through the gap to be sealed, which significantly increases the flow resistance.
  • the path extension is achieved by a surface structure of the piston and possibly also of the cylinder wall.
  • the surface of the piston preferably has a large number of circumferential depressions that are spaced apart from one another in the longitudinal direction of the piston. Absolute tightness is not possible with this contact-free design.
  • the labyrinth piston compressor comprising the labyrinth seal has the advantage that the labyrinth seal is contactless because the piston and the cylinder wall do not touch one another, and that therefore no lubrication is required between the piston and the cylinder wall.
  • Such a labyrinth piston compressor allows what is known as oil-free compression of a fluid because no lubricant, in particular no oil, is required to compress the fluid.
  • the piston of such a labyrinth piston compressor has no sealing rings because the labyrinth seal creates a seal.
  • the labyrinth piston compressor according to the invention has the advantage that it can be operated safely even if the temperature of the fluid to be sucked in and the temperature of the compressed fluid to be discharged have a large temperature difference of, for example, 100°C to 120°C or even more.
  • the piston compressor according to the invention is designed in such a way that the applied temperature differences do not result in any significant thermal stresses or any significant distortion of components of the piston compressor, or that the piston compressor is designed in such a way that an expansion of components caused by the applied temperature difference of the piston compressor is carried out in such a way that the individual components are hardly displaced relative to one another due to the temperature difference, which is particularly important for a labyrinth piston compressor, since the gap between the outer peripheral surface of the labyrinth piston and the inner surface of the cylinder facing the outer peripheral surface is particularly small.
  • the labyrinth piston compressor according to the invention can preferably be operated safely and reliably regardless of the temperature differences present.
  • the piston compressor according to the invention has the advantage that the at least one inlet valve and the at least one outlet valve are arranged in the cylinder cover, which results in the advantage that a fluid to be compressed flows directly into the cylinder interior after flowing through the inlet valve, or that a compressed fluid immediately leaves the cylinder interior when flowing through the outlet valve, so that the piston compressor has an extremely small or no dead space within which a temperature transfer between the fluid and the piston compressor could take place, so that the piston compressor has relatively few contact surfaces that could exchange heat with the fluid.
  • the piston compressor according to the invention thus preferably has, with the exception of the mandatory contact surfaces for the inflow of the fluid to be compressed, the compression of the fluid to be compressed and the discharge of the compressed fluid, preferably negligibly small or no additional contact surfaces and contact points between the piston compressor and the conveyed fluid, which limits heat transfer between the fluid and the piston compressor.
  • the cylinder and/or the piston of the piston compressor advantageously consists of a metal with a thermal conductivity in the range between 100 and 300 (W/m ⁇ K), preferably of aluminum or an aluminum alloy.
  • the relatively high thermal conductivity has The result is that during operation of the piston compressor, a temperature equilibrium is established in its components, the temperature differences of which are significantly smaller than the temperature differences between the inflowing and the compressed, outflowing fluid. It is particularly advantageous if the cylinder and the piston are made of the same material.
  • the inlet valve and the outlet valve are also arranged symmetrically in the cylinder with respect to a plane of symmetry running along a center line of the cylinder. This means that during operation of the piston compressor, an average temperature will be established in the area of the plane of symmetry, which lies between the temperature of the inflowing fluid and the temperature of the outflowing fluid, which reduces the maximum possible temperature differences that occur in the cylinder.
  • a flange or hose arranged at the inlet valve or outlet valve, which serve to supply or discharge the fluid has a small contact area with respect to the cylinder, which in turn reduces heat transfer between the flange or hose and the cylinder.
  • the piston compressor comprises a carrier housing in which a crankshaft and at least one crosshead are preferably arranged.
  • the piston compressor according to the invention comprises a spacer which is connected to the carrier housing and the cylinder in order to hold the cylinder in a defined position with respect to the carrier housing and to reduce any possible temperature flow between the cylinder and the carrier housing.
  • the spacer is connected to the cylinder in those areas where the average temperature or essentially the average temperature is present.
  • the temperature at the cylinder during operation of the piston compressor is The temperature differences occurring between the cylinder and the support housing in the spacer are kept within limits, with the spacer preferably being arranged in such a way that it has a heat distribution that is symmetrical to the plane of symmetry, with the result that little or no distortion of the spacer occurs due to the temperatures applied to the spacer.
  • the piston rod running between the support housing and the cylinder therefore also does not experience any deformation.
  • the cylinder and/or the piston are made of aluminum or an aluminum alloy, a metal that is therefore a very good heat conductor.
  • the very good heat conduction in turn has the advantage that during continuous operation of the piston compressor, an average temperature or an average operating temperature of the individual components of the compressor is established very quickly, thus avoiding temperature peaks.
  • the piston compressor according to the invention has the advantage that, in a preferred embodiment, it requires relatively few parts and that the moving parts can be selected to be relatively low in mass. This also results in the advantage that the piston compressor according to the invention can be operated at a high speed of, for example, up to 1800 revolutions per minute.
  • Fig.1 shows a longitudinal section through a piston compressor 1 comprising a cylinder 10 and a piston 20 arranged therein, comprising a carrier housing 60 with a crosshead 63 arranged therein with a bearing part 63a, wherein the crosshead 63 can be driven via a crankshaft 61 and a connecting rod 62, and comprising a spacer 40 with a support section 41, wherein the spacer 40 connects the cylinder 10 to the carrier housing 60 and, as in Figure 1 shown, carries the cylinder 10 when the piston compressor 1 is arranged upright.
  • the piston compressor 1 comprises a piston rod 24 which connects the crosshead 63 to the piston 20 and drives the piston 20.
  • the piston compressor 1 has a longitudinal axis L which extends along the piston rod 24 in the center of the piston rod 24.
  • the cylinder 10 comprises a first cylinder cover 11, a second cylinder cover 12, and a cylinder jacket 13 arranged therebetween.
  • the first cylinder cover 11 comprises an inlet valve receiving opening 11a and an outlet valve receiving opening 11b, in which an inlet valve 90 and an outlet valve 91 are arranged.
  • a flange 14 is connected to the opening 11a, 11b, the flange 14 serving to supply or discharge a fluid between the outside of the cylinder 10 and an interior 10a of the cylinder 10. Fluids can be supplied or discharged, for example, via a hose 15 connected to the respective flange 14.
  • the second cylinder cover 12 also comprises an inlet valve receiving opening 12a and an outlet valve receiving opening 12b with an inlet valve 90 or outlet valve 91 arranged therein.
  • the second cylinder cover 12 comprises a central section 12h having a passage opening 12g in which the piston rod 24 is arranged so as to be movable in its direction of travel L.
  • the cylinder 10 or the piston 20 is designed to be double-acting in that the piston 20 delimits a first cylinder interior 10a and a second cylinder interior 10b.
  • the cylinder jacket 13 could be dispensed with by making the first and second cylinder covers 11, 12 longer in the longitudinal direction L.
  • a first, a second and a third stuffing box chamber 50, 51.52 are arranged downstream of the central section 12h.
  • the spacer 40 has a spacer interior 40a in which an oil scraper packing 55, shown only schematically, comprising preferably a guide which encloses the piston rod 24.
  • an oil screen 54 is arranged on the piston rod 24.
  • the carrier housing 60 has a bore 60a which forms a sliding surface for the crosshead 63, so that the crosshead 63, the piston rod 24 connected to the crosshead 63 and the piston 20 connected to the piston rod 24 can move back and forth in the longitudinal direction L.
  • the sliding surface for the crosshead is lubricated, preferably with oil, although this lubrication is not shown in detail.
  • the cylinder 10 and/or the piston 20, and preferably also the support housing 60 and the crosshead 63 are made of a metal with a thermal conductivity in the range of preferably between 100 and 300 (W/m K), preferably aluminum or an aluminum alloy.
  • the cylinder 10 and the piston 20, and preferably also the support housing 60 and the crosshead 63 are made of the same material so that they have the same properties with regard to thermal expansion.
  • Figure 2 shows a detailed view of the piston compressor 1 according to Figure 1 , essentially the cylinder 10, the piston 20, the flanges 14 and the inlet and outlet valves 90, 91.
  • the cylinder 10 and the piston 20 are designed to be single-acting, for example by arranging an inlet valve 90 and an outlet valve 91 in only the first cylinder cover 11.
  • the cylinder 10 and the piston 20 are particularly advantageous, as shown in Figure 2 shown, double-acting, with a first cylinder interior 10a, a second cylinder interior 10b and two inlet valves 90 and two outlet valves 91.
  • an inlet valve 90 and an outlet valve 91 are arranged at least in the first cylinder cover 11 or in the second cylinder cover 12, and preferably as in Figure 2 shown in both cylinder covers 11,12 one inlet valve 90 and an outlet valve 91 is arranged.
  • the inlet valve 90 and the outlet valve 91 are arranged symmetrically with respect to a plane of symmetry S running in the longitudinal direction L along the piston rod 24.
  • both inlet valves 90 and both outlet valves 91 are as in Figure 2 shown arranged on the same side of the cylinder 10, that is, as in Figure 2 shown, both to the left and both to the right of the plane of symmetry S.
  • the piston compressor according to the invention is particularly suitable for compressing a fluid whose inlet fluid F E flowing in via the inlet valve 90 and whose outlet fluid F A flowing out via the outlet valve 91 have a large temperature difference of, for example, between 100°C and 150°C.
  • the inlet fluid F E for example evaporation gas from liquid natural gas
  • the outlet fluid F A can have a temperature of -40 °C, so that the temperature difference is 120 °C.
  • the symmetrical arrangement of the inlet valve 90 and the outlet valve 91 with respect to the plane of symmetry S has the advantage that the cylinder 10 and the piston 20 have an average temperature during operation in the area of the plane of symmetry S or the longitudinal axis L running along the piston rod 24, whereby the temperature of the cylinder 10 and the piston 20 perpendicular to the longitudinal axis L usually decreases towards the inlet valve 90 and increases towards the outlet valve 91.
  • the cylinder 10 preferably has only small temperature differences.
  • the cylinder 10 and the piston 20 have an average temperature in the area of the longitudinal axis L during operation, the cylinder 10, the piston 20 and the piston rod 24 experience no or negligible distortion caused by temperature differences in these parts, or by temperature differences caused by the temperature differences. Length changes.
  • the cylinder 10 and/or the piston 20 consists of a material with good heat conduction, for example aluminum, which has the advantage that the temperature differences present at the cylinder 10 and the piston 20 during operation are reduced.
  • the piston compressor according to the invention is advantageously operated at ambient temperature. If the piston compressor according to the invention is used to compress evaporative gas from liquid natural gas, the outer surface of the cylinder 10 is heated with air at ambient temperature, which further reduces temperature differences at the cylinder 10, particularly if the cylinder 10 or at least the cylinder covers 11, 12 are made of a material that conducts heat well.
  • a gas space is understood to be the space between a fluid supply line 15 and the inlet valve 90 or the space between the outlet valve 91 and a fluid discharge line 16.
  • the piston compressor 1 according to the invention advantageously has no or a very small gas space in that the fluid supply line 15 or a flange 14 is arranged in the fluid flow direction F immediately before the inlet valve 90, via which the fluid is supplied to the cylinder 10 from the outside, or in that an outward-leading fluid discharge line 16 or a flange 14 is arranged in the fluid flow direction F immediately after the outlet valve 91, via which the fluid is discharged from the cylinder 10 to the outside.
  • the pumped fluid is therefore no longer in direct heat-conducting contact with the cylinder 10 until immediately before the inlet valve 90 or immediately after the outlet valve 91. This has the consequence that the cylinder 10 is cooled to a lesser extent.
  • At least one of the components inlet valve 90, outlet valve 91 and flange 14 is designed such that it has an increased thermal conduction resistance to the cylinder cover 11, 12 in order to extract heat from the cylinder cover 11, 12 only to a reduced extent due to the cool fluid flowing through the inlet valve 90, the outlet valve 91 and/or the flange 14.
  • Figure 3 shows a detailed view of an embodiment for increasing the thermal resistance.
  • the outlet valve 91 does not lie on the first cylinder cover 11 over its entire surface, but only partially over the partial surfaces 91a, which increases the thermal resistance between the outlet valve 91 and the first cylinder cover 11.
  • the inlet valve 90 could also be arranged in the first or second cylinder cover 11, 12.
  • FIG. 3 Another possibility for increasing the thermal resistance is as in Figure 3 shown in that the flange 14 does not rest on the first cylinder cover 11 over its entire surface but only partially over the partial surfaces 14a, which increases the thermal resistance between the flange 14 and the first cylinder cover 11.
  • the flange 14 could also be arranged in the second cylinder cover 12.
  • the piston compressor 1 according to the invention is advantageously operated at ambient temperature, so that the cylinder 10 is heated by the ambient air during the conveying and compression of, for example, exhaust steam gas, wherein the increase in the thermal resistance described above results in the advantage that the cylinder 10 is cooled to a reduced extent due to the fluid F flowing through it, so that the cylinder 10 has a higher temperature and preferably also a more uniform temperature distribution during operation, which, for example, reduces the risk of warping of the components of the piston compressor 1 due to the applied temperature differences, in particular warping of the cylinder 10, the piston 20, the piston rod 24 or the spacer 40.
  • the inner side of the first or second cylinder cover 11, 12 and the outer surface of the first or second piston cover 21, 22 are designed to be mutually adapted in such a way that the so-called dead space remains as small as possible.
  • At least one of the two piston covers 21, 22 has a piston end face 21a, 22a that projects towards the associated cylinder cover 11, 12, in particular a convex one, wherein the associated cylinder cover 11, 12 has a correspondingly projecting cylinder cover outer side 11c, 12c or a cylinder cover inner side 11d, 12d that recedes accordingly with respect to the piston end face 21a, 22a.
  • the first cylinder interior 10a corresponds to the clearance space in the uppermost position of the piston 20, which, as can be seen from Figure 3 obviously, is very small.
  • first cylinder cover 11 and/or the second cylinder cover 12 could have an end face running perpendicular to the longitudinal axis L, in which the inlet valve 90 and the outlet valve 91 are arranged.
  • first cylinder cover 11 and/or the second cylinder cover 12 are as in Figure 2 shown designed in such a way that the inlet valve 90 and the outlet valve 91 are arranged in the cylinder cover 11, 12 at an incline with respect to the plane of symmetry S. This makes it possible to use valves 90, 91 with a larger diameter, which reduces their flow resistance.
  • the Figures 4 and 5 show the same cylinder 10 as in Figure 2 , however, not in a section but in two different side views.
  • the cylinder 10 comprises the first cylinder cover 11, the cylinder jacket 13 and the second cylinder cover 12.
  • the flanges 14 are arranged.
  • the cylinder 10 is firmly connected to the carrier housing 60 via a spacer 40 and is arranged at a distance from the carrier housing 60.
  • the spacer 40 comprises two support arms 42, 43 arranged symmetrically with respect to the plane of symmetry S.
  • the second cylinder cover 12 comprises two fastening points 12e, 12f, which are each firmly connected to a support arm 42, 43.
  • Each of the two fastening points 12e, 12f is preferably designed identically in the circumferential direction and, as in Figure 4 shown, has a width C in the circumferential direction in the range of preferably between 10° and 30°.
  • Figure 4 the course of the section line BB and the course of the symmetry plane S are shown.
  • Figure 5 the course of the section line AA and the course of the second symmetry plane S 2 are shown.
  • the fastening points 12e, 12f preferably run as in Figure 4 with the fastening point 12f, essentially perpendicular to the plane of symmetry S and are arranged symmetrically to the plane of symmetry S.
  • the point S 3 shows the intersection point of the fastening point 12f with the plane of symmetry S.
  • the fastening point 12f preferably runs symmetrically with respect to the point S 3 or symmetrically with respect to the plane of symmetry S.
  • the cylinder 10 has an average temperature in the region of the plane of symmetry S or in the region of the point S 3 during operation of the piston compressor 1, wherein due to the symmetrical arrangement the same temperature is present at both fastening points 12e, 12f, or the cylinder 10 has the same temperature, so that the first support arm 42 and the second support arm 43 also have the same temperature at the two fastening points 12e, 12f.
  • the symmetrical design of the cylinder 10 and the flanges 14 attached to the cylinder 10, as well as the symmetrical arrangement of the two fastening points 12e, 12f, as well as the symmetrically designed support arms 42, 43 of the spacer 40 result in the advantage that the support arms 42, 43 on the two Fastening points 12e, 12f have the same temperature, so that no mutual thermal distortion occurs on the two support arms 42, 43.
  • the input fluid F E and the output fluid F A can have a considerable temperature difference, so that the corresponding flanges 14 and also the cylinder 10 and possibly the piston 20 in the direction of travel C can have a temperature difference, which could at most lead to a distortion of the cylinder or a distortion of its components, in particular in the direction of travel C.
  • a distortion has no or a negligible influence on the point S 3 or on the support arms 42, 43, so that the cylinder 10 is held in a defined position by the spacer 40 during operation of the piston compressor 1.
  • the piston rod 24 also passes through the passage opening 12g of the second valve cover 12 in the area of the plane of symmetry S, an area of the valve cover 12 which also has a medium temperature, so that no or only very slight thermally induced distortion should occur between the passage opening 12g and the piston rod 24.
  • the spacer 40 is U-shaped, comprising a first support arm 42 and a second support arm 43.
  • the spacer 40 could also have more support arms, for example four, six or eight, which are connected to the second cylinder cover 12 and which are preferably arranged symmetrically with respect to the plane of symmetry S.
  • the second stuffing box chamber 51 and the third stuffing box chamber 52 are not shown.
  • Figure 6 essentially shows the cylinder 10 and the piston 20 without the flanges 14 in a section along the section line AA.
  • Figure 7 essentially shows the cylinder 10 and the piston 20 without the flanges 14 in a section along the section line BB.
  • the cylinder 10 comprises at least three parts, the first cylinder cover 11, the second cylinder cover 12 and a preferably tubular cylinder jacket 13, wherein the cylinder jacket 13 is arranged between the first cylinder cover 11 and the second cylinder cover 13.
  • the piston 20 comprises at least three parts, a first piston cover 21, a second piston cover 22 and a piston skirt 23 arranged between the first and second piston covers 21, 22.
  • This layered structure of the cylinder and/or piston enables particularly favorable maintenance because during maintenance only those parts that could show significant wear need to be replaced, for example the cylinder skirt 13 and the piston skirt 23.
  • the piston skirt 23 at least partially has a labyrinth-shaped outer surface 23a, so that the piston compressor 1 is designed as a labyrinth piston compressor.
  • At least one sealing ring is arranged on the piston skirt 23, the piston skirt 23 preferably having at least one circumferential groove in which the sealing ring is arranged, so that the piston compressor 1 is designed as a ring-sealed piston compressor 1.
  • the second cylinder cover 12 has fastening points 12e, 12f, preferably arranged on its outer edge 12i, to which the support arms 42, 43 are fastened via a fastening means (not shown), preferably a screw.
  • the fastening points 12e, 12f are preferably arranged mutually symmetrically to the plane of symmetry S.
  • At least one of the two piston covers 21,22 has a protruding, in particular convex piston face 21a, 22a, wherein the associated cylinder cover 11, 12 has a correspondingly protruding cylinder cover outer side 11c, 12c or a cylinder cover inner side 11d, 12d which recedes accordingly with respect to the piston face 21a, 22a, as is shown for example in Figure 2 is shown.
  • the second cylinder cover 12 has in its center a passage opening 12g running in the longitudinal direction L, along which the piston rod 24 runs, wherein preferably in the longitudinal direction L downstream of the passage opening 12g, outside the cylinder cover 12, at least one stuffing box chamber 50 is arranged and preferably a plurality of stuffing box chambers are arranged.
  • At least one of the inlet valve 90, the outlet valve 91 and the flange 14 does not rest with the entire possible surface on the first or second cylinder cover 11, 12, but only partially rests, i.e. with a part of the possible total surface, on the first or second cylinder cover 11, 12 in order to increase the thermal conduction resistance between the inlet valve 90, the outlet valve 91, the flange 14 and the first or second cylinder cover 11, 12.
  • Figure 8 shows the piston compressor 1 in a side view.
  • This comprises two cylinders 10 with pistons 20 arranged therein, each piston 20 being connected to the support housing 60 via a spacer 40, and each piston rod 24 being driven by a common crankshaft 61.
  • An oil collecting pan 64 is arranged below the support housing 60.
  • the piston compressor 1 can also have just a single cylinder 10 with piston 20, or a plurality of cylinders 10 with corresponding piston 20, for example between three and ten cylinders 10.
  • Figure 9 shows a compressor unit 80 comprising a piston compressor 1, an electric motor 81, a supply manifold 85, which is connected to the fluid supply line 15, and a discharge manifold 86, which is connected to the fluid discharge line 16.
  • the fluid supply line 15 and the fluid discharge line 16 are preferably designed to be elastic in order to compensate for temperature-related expansions, wherein these lines 15, 16 consist, for example, of a metal mesh.
  • the piston compressor 1 comprises a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a piston rod 24 running in a longitudinal direction L which connects the crosshead 63 to the piston 20, wherein the spacer 40 comprises a plurality of support arms 42, 43, wherein the support arms 42, 43 are connected to the cylinder 10 and support it.
  • the cylinder 10 advantageously comprises a plurality of fastening points 12e, 12f which are arranged symmetrically with respect to the longitudinal axis L and to which the support arms 42, 43 are fastened.
  • the piston compressor has a plane of symmetry S running in the longitudinal direction L along the piston rod 24, wherein the fastening points 12e, 12f and the support arms 42, 43 are arranged symmetrically with respect to the plane of symmetry S.
  • the spacer 40 is U-shaped, with two support arms 42, 43 running in the longitudinal direction L, wherein the cylinder 10 has two fastening points 12e, 12f to which the support arms 42, 43 are fastened.
  • each fastening point 12e, 12f has a width C in the range between 10° and 30°.
  • the cylinder 10 advantageously comprises an inlet valve 90 and an outlet valve 91, the inlet valve 90 and the outlet valve 91 being arranged symmetrically with respect to the plane of symmetry S.
  • the cylinder 10 advantageously comprises a first cylinder cover 11 and a second cylinder cover 12, both the first and the second cylinder covers 11, 12 comprising an inlet valve 90 and an outlet valve 91, so that the cylinder 10 and the piston 20 are designed to be double-acting.
  • a plurality of cylinders 10 with pistons 20 arranged therein are advantageously arranged at a distance from one another on the carrier housing 60 and are each connected to the carrier housing 60 via a separate spacer 40.
  • each piston 20 is assigned a piston rod 24, the support housing 60 being designed as a monoblock, and the monoblock having a number of bores corresponding to the number of piston rods 45, in each of which a crosshead 63 is slidably mounted, each piston 20 being connected to the associated crosshead 63 via a piston rod 20.
  • the monoblock and the crosshead 62 consist of a metal with a thermal conductivity in the range between 100 and 300 (W/m ⁇ K), preferably aluminum or an aluminum alloy.
  • the cylinder 10 and/or the piston 20 consists of a metal with a thermal conductivity in the range between 100 and 300 (W/m ⁇ K), preferably aluminum or an aluminum alloy.
  • the piston compressor 1 comprising a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a piston rod 24 running in a longitudinal direction L which connects the crosshead 63 to the piston 20, is advantageously designed in such a way operated in such a way that heat energy, caused by a heat difference between the cylinder 10 and the support housing 60, is exchanged via a plurality of support arms 42, 43.
  • an inlet fluid F E is supplied to the cylinder 10 via an inlet valve 90, and the fluid in the cylinder 10 is expelled from the cylinder 10 as an outlet fluid F A via an outlet valve 91, the inlet valve 90 and the outlet valve 91 being arranged symmetrically with respect to a plane of symmetry S running along the longitudinal direction L of the piston rod 24, so that the cylinder 10 is heated to an average temperature during the conveyance of the fluid in the region of the plane of symmetry S, which temperature lies between the temperature of the inlet fluid F E and the outlet fluid F A , the support arms 42, 43 being connected to the cylinder 10 in the region of the plane of symmetry S via fastening points 12e, 12f.
  • the two center points S 3 between the fastening points 12e, 12f are heated to essentially the same temperature during the conveying of the fluid.
  • the piston rod 45 runs in the region of the plane of symmetry S, and this is heated to essentially the same temperature as the fastening points 12e, 12f during the conveying of the fluid.
  • the piston compressor 1 shown comprises a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a piston rod 24 running in a longitudinal direction L which connects the crosshead 63 to the piston 20, wherein the spacer 40 comprises a plurality of support arms 42, 43 running in the longitudinal direction L, wherein the support arms 42, 43 are each individually connected to the cylinder 10 towards the cylinder 10.
  • the cylinder 10 has a plurality of fastening points 12e, 12f, wherein a support arm 42, 43 is fastened to each fastening point 12e, 12f.
  • the fastening points 12e, 12f are arranged symmetrically with respect to the longitudinal direction L.
  • the method for operating a piston compressor 1 comprises a cylinder 10 and a piston 20 arranged therein, a support housing 60 with a crosshead 63 mounted in the support housing 60, a spacer 40 which connects the cylinder 10 to the support housing 60, and a piston rod 24 running in a longitudinal direction L which connects the crosshead 63 to the piston 20, wherein the spacer 40 comprises a plurality of support arms 42, 43 running in the longitudinal direction L, wherein the support arms 42, 43 are each individually connected to the cylinder 10 towards the cylinder 10 via fastening points 12e, 12f, so that heat energy, due to a heat difference between the fastening points 12e, 12f, is not exchanged directly in the circumferential direction to the longitudinal direction L between the fastening points 12e, 12f, but is exchanged via the support arms 42, 43 running in the longitudinal direction L.
  • the inlet fluid F E is preferably supplied at a temperature in the range between -162°C and -40°C, and the outlet fluid F A is preferably heated by compression by a temperature difference in the range between 100°C and 150°C.
  • the fastening points 12e, 12f in the area of the symmetry plane S each have a center point S 3 , which during the The fluid must be heated to essentially the same temperature during pumping.
  • the spacer 40 is U-shaped, with a support section 41 and two support arms 42, 43 running in the longitudinal direction L, wherein heat energy is exchanged between the cylinder 10 and the carrier housing 60 via the support arms 42, 43 and the support section 41.
  • each fastening point (12e, 12f) has a width C in the range between 10° and 30° in the circumferential direction of the cylinder 10, wherein each fastening point 12e, 12f is arranged symmetrically to the center S 3 , so that heat energy is transferred from the respective support arm 42, 43 along the fastening point 12e, 12f in the circumferential direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (13)

  1. Compresseur à piston labyrinthe (1) comprenant un cylindre (10), un piston (20) disposé dans le cylindre (10), ainsi qu'une tige de piston (24), la tige de piston (24) s'étendant dans une direction longitudinale (L) et étant reliée au piston (20), et le piston (20) étant mobile en va-et-vient à l'intérieur du cylindre (10) dans la direction longitudinale (L), dans lequel le cylindre (10) comprend un premier couvercle de cylindre (11), dans lequel une soupape d'admission (90) ainsi qu'une soupape d'échappement (91) sont disposées dans le premier couvercle de cylindre (11), et dans lequel la soupape d'admission (90) et la soupape d'échappement (91) sont disposées symétriquement par rapport à un plan de symétrie (S) s'étendant dans la direction longitudinale (L) le long de la tige de piston (24), la soupape d'admission (90) ainsi que la soupape d'échappement (91) étant disposées dans le couvercle de cylindre (11, 12) de manière inclinée par rapport au plan de symétrie (S), caractérisé en ce que, dans le sens d'écoulement (F) d'un fluide transporté, une bride (14) menant vers l'extérieur est disposée directement avant la soupape d'admission (90) ou directement après la soupape d'échappement (91) dans le sens d'écoulement (F) du fluide, afin d'amener le fluide au cylindre (10) depuis l'extérieur ou d'évacuer le fluide du cylindre (10) vers l'extérieur.
  2. Compresseur à piston à labyrinthe selon la revendication 1, caractérisé en ce que le cylindre (10) comprend un deuxième couvercle de cylindre (12), en ce qu'une soupape d'admission (90) ainsi qu'une soupape d'échappement (91) sont également disposées dans le deuxième couvercle de cylindre (12) de manière symétrique par rapport au plan de symétrie (S) et en ce que le cylindre (10) et le piston (20) sont ainsi conçus à double effet.
  3. Compresseur à piston labyrinthe selon l'une quelconque des revendications précédentes, caractérisé en ce que le cylindre (10) et/ou le piston (20) est constitué d'un métal ayant une conductivité thermique comprise entre 100 et 300 (W/m - K), de préférence de l'aluminium ou un alliage d'aluminium.
  4. Compresseur à piston labyrinthe selon l'une des revendications précédentes, caractérisé en ce que le deuxième couvercle de cylindre (12) est relié à un boîtier de support (60) par l'intermédiaire de une entretoise (40) et est maintenu à distance du boîtier de support (60) par l'entretoise (40), et en ce que l'entretoise (40) comprend au moins deux bras de support (42, 43) disposés symétriquement par rapport au plan de symétrie (S) et s'étendant dans la direction longitudinale (L), qui sont reliés au deuxième couvercle de cylindre (13).
  5. Compresseur à piston labyrinthe selon la revendication 4, caractérisé en ce que le deuxième couvercle de cylindre (12) présente des points de fixation (12e, 12f) disposés sur son bord extérieur (12i), sur lesquels sont fixés les bras de support (42, 43), et en ce que les points de fixation (12e, 12f) sont disposés symétriquement par rapport au plan de symétrie (S), de préférence essentiellement perpendiculairement au plan de symétrie (S).
  6. Compresseur à piston labyrinthe selon la revendication 5, caractérisé en ce que l'entretoise (40) est conçue en forme de U, avec deux bras de support (42, 43) s'étendant dans la direction longitudinale (L), et en ce que le deuxième couvercle de cylindre (12) présente deux points de fixation (12e, 12f).
  7. Compresseur à piston labyrinthe selon la revendication 5 ou 6, caractérisé en ce que chaque point de fixation (12e, 12f) présente une largeur (C) comprise entre 10° et 30° dans la direction circonférentielle du deuxième couvercle de cylindre (13).
  8. Compresseur à piston labyrinthe selon l'une des revendications précédentes, caractérisé en ce que le cylindre (10) comprend au moins trois parties, le premier couvercle de cylindre (11), le deuxième couvercle de cylindre (12) ainsi qu'une enveloppe de cylindre (13) en particulier de forme tubulaire, l'enveloppe de cylindre (13) étant disposée entre le premier couvercle de cylindre (11) et le deuxième couvercle de cylindre (13).
  9. Compresseur à piston à labyrinthe selon l'une des revendications précédentes, caractérisé en ce que le piston (20) comprend au moins trois parties, un premier couvercle de piston (21), un deuxième couvercle de piston (22) ainsi qu'une enveloppe de piston (23) disposée entre le premier et le deuxième couvercle de piston (21, 22), l'enveloppe de piston (23) présentant au moins partiellement une surface extérieure (23a) en forme de labyrinthe.
  10. Compresseur à piston à labyrinthe selon la revendication 9, caractérisé en ce qu'au moins l'un des deux couvercles de piston (21, 22) présente une surface frontale de piston (21a, 22a), en particulier convexe, s'étendant en saillie vers le couvercle de cylindre (11, 12) associé, et en ce que le couvercle de cylindre (11, 12) associé présente une face extérieure de couvercle de cylindre (11c, 12c) en saillie correspondante ou une face intérieure de couvercle de cylindre (11d, 12d) en retrait correspondant par rapport à la surface frontale de piston (21a, 22a).
  11. Compresseur à piston à labyrinthe selon l'une des revendications précédentes, caractérisé en ce que le deuxième couvercle de cylindre (12) présente en son centre une ouverture de passage (12g) s'étendant dans la direction longitudinale (L), le long de laquelle s'étend la tige de piston (24), au moins une chambre de presse-étoupe (50) étant disposée dans la direction longitudinale (L) en aval de l'ouverture de passage (12g), à l'extérieur du couvercle de cylindre (12).
  12. Compresseur à piston labyrinthe selon l'une des revendications précédentes, caractérisé en ce qu'au moins un de la soupape d'admission (90), de la soupape d'échappement (91) et de la bride (14) n'est en contact que sur une partie de sa surface avec le premier ou le deuxième couvercle de cylindre (11, 12) afin d'augmenter la résistance à la conduction thermique entre la soupape d'admission (90), la soupape d'échappement (91), la bride (14) et le premier ou le deuxième couvercle de cylindre (11, 12).
  13. Compresseur à piston labyrinthe selon l'une des revendications 4 à 12, caractérisé en ce qu'une pluralité de cylindres (10) avec un piston (20) disposé à l'intérieur sont disposés sur un boîtier de support commun (60) et sont entraînés par un vilebrequin commun (61) disposé dans le boîtier de support (60).
EP19783448.4A 2018-09-24 2019-09-24 Compresseur à piston labyrinthe Active EP3857068B1 (fr)

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EP18196407 2018-09-24
PCT/EP2019/075774 WO2020064781A1 (fr) 2018-09-24 2019-09-24 Compresseur à piston à labyrinthe

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EP (1) EP3857068B1 (fr)
JP (1) JP7564095B2 (fr)
KR (1) KR20210063407A (fr)
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Publication number Priority date Publication date Assignee Title
CH647046A5 (en) * 1982-01-21 1984-12-28 Sulzer Burckhardt Maschinenfab Piston compressor having at least one labyrinth piston

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KR20210063407A (ko) 2021-06-01
JP7564095B2 (ja) 2024-10-08
US20210404454A1 (en) 2021-12-30
EP3857068A1 (fr) 2021-08-04
WO2020064781A1 (fr) 2020-04-02
JP2022502596A (ja) 2022-01-11

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